Valving ring for fluid pump having pump pistons



March 22, 1960 H. M. PURCELL 2,929,398

VALVING RING FOR FLUID PUMP HAVING PUMP PISTONS Original Filed Nov. 16 1955 5 Sheets-Sheet l a v I 9 L! L 42 1-,.- l 2 9a 27 g a so as 5 I8 3: 46 9 as 7o 47 39 I 6 41 M 535;:

/ l8 2 Me I f a 3 I 32 Fig.1 r\\ a BY l(/ w INVENTOR. HOWARD M. PURCELL March 22, 1960 PURCELL 2,929,398

VALVING RING FOR FLUID PUMP PAVING PUMP PISTONS Original Filed Nov. 16 1955 3 Sheets-Sheet 2 INVENTOR. HOWARD M. PURCELL BY #M I I e I "W- 4 March 22, 1960 H. M. PURCELL 2,929,393

VALVING RING F OR FLUID PUMP PAVING PUMP PISTONS 5 Sheets-Sheet 3 Original Filed Nov 16 1955 INVENTOR- HOWARD M. PURCELL BY i m VALVI NG RING FOR FLUID PUlVlP HAVING PUlVIP PISTONS Howard M. Purcell, Mount Gilead, Ohio, assignor, by mesne assignments, to Koehrin Company, Milwaukee, Wis, a corporation of Wisconsin Claims. (Cl. 137-512) The invention relates in general to fluid pumps and more particularly to fluid pumps having pump pistons which are actuated on an intake stroke by fluid extendible means responsive to a fluid pressure which is produced by a secondary pump and to means which includes a valving ring for collapsing all or a portion of the pump pistons thereby enabling the pump to be driven and selectively operated to pump fluid under pressure or to idle without pumping fluid under pressure.

This application is a division of my application, Serial No. 547,106, filed November 16, 1955.

An object of the invention is to provide an improved valving ring for a fluid pump having pump pistons actuated on a discharge stroke by cam means with a means for collapsing or rendering the pump pistons inelfective to perform the pumping operation.

Another object of the invention is to provide a fluid pump having a plurality of pump pistons with a valving ring wherein a portion of the pump pistons may be collapsed and rendered ineffective to perform the pumping operation and the remainder of the pump pistons will still be effective to perform the pumping operation.

Other objects and a fuller understanding of the invention may be had by referring to the following description and claims taken in combination with the accompanying drawings in which:

Figure 1 is a side elevation view in section of a fluid P p;

Figure 2 is a view taken along the line 22 of Figure 1;

Figure 3 is a view taken along the line 3-3 of Figure 1;

Figure 4 is a side elevation view in section of a pump similar to that which is shown in Figure 1 but illustrating a modification of the pump of Figure l incorporating the valving ring illustrating the principle of the invention;

Figure 5 is a view taken along the line 5-5 of Figure 4;

Figure 6 is a view taken along the line 6-6 of Figure 4;

Figure 7 is an isometric view with a portion thereof cut away showing the details of the valving ring which is used in conjunction with the fluid pump of Figure 4.

Figure 8 is a view taken along the line 88 of Figure 7; and

Figure 9 is an enlarged fragmentary view taken along the same line as Figure 3 and showing the secondary pump which is shown in Figure 3 in more detail and in a slightly different position.

The fluid pump of the type in which the improved valving ring may be used is indicated generally by the reference numeral 15. The pump comprises a primary housing 16 having a cylindrically shaped insert member 18 extending therein. The insert member 18 has an end portion 19 and a central axis indicated by the dot-dash lines 20. A rotor 23 surrounds the insert member '18 and has a plurality of axially extending pump cylinders therein. All of the pump cylinders within the rotor-23 have been designated by the same reference 2,929,398 e, 7 Pa.'iented Mar. 22, teen numeral 24. The rotor 23 is adapted forrotation about the insert member 18 and hence about the central axis 20 of the insert member 18. Each of the pump cylinders 24 is provided with a first and a second pump piston 27 and 28, respectively. Each of the first pump pistons 27 has a first cam follower 30 on an end portion thereof and each of the second'pump pistons 23 hasasecond cam follower 31 attached to an end portion. Each of the cam followers 30 and 31 are in communication with the interconfines of the primary housing 16., Cam means 33 which include a first and a second cam member 34 and 35, respectively, are engageable with the first and second cam followers 30 and 31, respectively, of each of the first and second pump pistons 27 and 28, for urging the pump pistons inwardly toward each other on a discharge stroke. The insert member 18 is provided with an intake passageway 38 which provides the fluid pump 15 with low pressure fluid and a first and a second discharge passageway 39 and 40, respectively, which provide for the exit of high pressure fluid from the fluid pump. 'As will be noted in Figure l the first and second discharge passageway 39 and 49, respectively, join together at an end portion of the insert member 13 in a chamber 41 and thereafter fluid travels from the pump in a single discharge conduit 42. Port means 46 are provided within the rotor 23 for providing alternate communicat'ion between each of the pump cylinders 24 and the intake and discharge passageways. 47 mounted on bearings 48 and 49 and driven by any suitable power source, not shown herein, is operably connected to the rotor 23 bymeans of a connection member 51 for rotating the rotor 23 about the central axis 20.

Fluid extendible means or fluid means are provided within each of the pumping cylinders 24 for maintaining the cam followers 30 and 31, respectively on each of the pump pistons inengagement with the first and second cam members 34 and 35, respectively, during the intake stroke of each of the first and second pump pistons 27 and 28, respectively. The fluid extendible means 50 include a fluid chamber 53 within each of the first pump pistons 27 in each of the pump cylinders 24 and a piston rod 54 in each of the pump cylinders24. The piston rod 54 has a first and a second end portion 55 and 56, respectively. The first end' portion communicates with the fluid chamber 53in each of the first pump pistons by way of an aperture 59 in each of the first pump pistons. The piston rod 54 slidably resides in the aperture 59 and extends axially within the pump cylinder 24 and the second end portion 56 thereof is engageable with or maybe fixedly attached to the second pump piston 28 in each of the pump cylinders 24.

A secondary control pump 63 shown in Figures 1, 3 and 9 is located within the end portion 19 of the insert member 18. The secondary control pump 63 includes wall means 64 which define a cylindrically shaped secondary control pumping housing 65. The secondary control pump housing is located coaxially with the insert member 18. A cylindrically shaped secondary control pump member 68 is mounted eccentrically within the secondary control pump housing 65 for rotation therein. A chamber forming member 70 extends from the wall means 64 and engages the secondary control pump member 68 thereby forming an input and an exhaust chamber 72 and 73, respectively, within the secondarypump.

A spring 75 urges" the chamber forming member 70 into engagement with the secondary control pump member 68 thereby forming the input and exhaust chambers at all times withinrthe secondary control pump 63. Figure 9 is enlarged to better show the details of the secondary control pump '63'and shows the secondary control pump member 68 moved angularly approximately degrees A drive shaft from the position in Figure 3. Input conduit means 77 connect the input chamber 72 of the secondary control pump 63 and the intake passageway 38 which is located within the insert member 18;. fl'he input conduit means 77 are best seen in Figures 2 and 3 but in Figure I the position of the input conduit means as it connects with the intake passageway 38 is indicated by the dot-dash lines 81. This provides a means for supplying fluid to the secondary control pump. In actual operation and practice, however, the secondary pump '63 may operate without the input conduit means 77. It ispossible to supply fluid to the secondary control pump by. the normal leakage and slippage of fluid from the discharge passagea ways 39 and 40 which leak into the primary housing 16 along the innerface of the various mating surfaces such as the surface between the insertrnen'tber lfl and the rotor Exhaust n t m@! ...'/3,I=9P Q his xha chamber 73 of the secondary contrrgl '63 and the fluid chamber 53 in each r henrst 'j pistons :47 w i r located in man the Pum s m n- 2 a relief pressure valve selectively; connects the exhaust conduit means '78 to the interior of the primary "housing 16 so as to prevent excessive pressure buildup in the ex haust conduit means 78. Connection. means' 80 which include an extensiorr'of the drive shaft '47 areprovided for connecting the secondary control pump member 68 to the same source of power that drives the rotor 23, Upon actuation of the drive shaft 47 in addition to rotating the rotor 23 the secondary control pump "member '68 is rotated eccentrically within the secondary housing 65 whereby fluid under pressure is delivered by way of the exhaust conduit means 78 to the fluid chamber 53 in each of the first pump pistons27'. This fluid pressure within the fluid chamber 53 "acts upon an end face 83 of the piston rod 54 and against an end wall 84 of the fluid chamber 53 whereby the first and secondpump pistons 27 and 28 in each of the pump cylinders 24 are urged axially outwardly and the cam followers 30 and 31 are maintained in engagement with the first and second 'cam members 34 and 35, respectively, on the intake stroke of the pump pistons.

Piston collapsing conduit means 90 are provided within the pump and connects the exhaustcon duit means 78 to a low pressure system 91. The low pressure system 91 is preferably anysuitable sump which may be at normal atmospheric pressure. In event the low pressure system is at a lower pressure ,thanthe pressure at which the secondary pump 63 delivers. fluid therefrom. Valve means 93 are interposed withinthe piston collapsing conduit means 90 and cooperate therewith. The valve means 93 are movable between a first and a second position. The valve means in the first position permits fluid communication between the exhaust conduitmeans 78 and the low pressure system 91 whereby fluid which is delivered by the secondary controlpump 6,3 is exhausted to the low pressure area 91. In this position the fluid pressure within the fluid chamber 53is greatly lessened if not completely reduced and the fluid extendible means are prevented from accomplishing their normal function. As a result the pump pistons in each of the pump cylinders are collapsed from engagement with the cam means 33. The collapsed position is when the first and second pump pistons have reached the end of their discharge stroke. In the positionindicated in Figure 1 the first and second pump pistons 27 and 28 are at the end of their discharge stroke and ready to start their intake stroke. The end of the intake stroke will come about when the rotor has rotated 90 degrees from the position shown in Figure 1. When the valve means 93 are inthe secondv position they prevent fluid communication between the exhaust conduit means 78 or the second control pump 63 andlow pressure'systern 9 1. In this posi tion the fluid pressure which is producedfbythe'secondary pump is communicatedltofthefl d cha'mhers 53finjeach of the first pump pistons .27 and a a result the lipid ex tendible means 50 are actuated and the first and second pump pistons are maintained in engagement with the cam means 33.

Pressurizing means 96 for pressurizing the interior confines of the primary housing 16 have been provided. The pressurizing means 96 which have been herein disclosed includes a tank 97 connected to the interior of the primary housing by way of a pipe 98. The tank 97 may be filled with any type of fluid but preferably the particular fluid which the pump 15 is pumping and the pressure within the housing will depend on the height of the tank 97 above the pump 15. Since fluid pressure acts equally in all directions there will be a force exerted against a first surface 161 on the cam followers 30 and 31, respectively, tending to move the cam followers against the cam means 33 and also an equal force per unit area acting upon a second surface 102 of the cam followers 30 and 31, respectively, tending to move the pump pistons inwardly toward each other. The resultantforce will be a force inwardly on the pump pistons because the "second surface area 192 is greater than the first surface area 101. Therefore when the valve means 93 are in the first position which renders the fluid extendiblemean's ineffective the resultant force on the pump pistons caused by pressurizing the primary housing will tend to hold the first and second pump pistons positively in the collapsed position.

It will thus be seen that while the drive shaft 47 is driving the rotor 23 and the secondary control pump 63 the pump pistons may be collapsed or rendered ineffective to accomplish the pumping operation by merely moving the valve means 93 to the first condition. This transfers the fluid delivered by the secondary pump 63 to the low pressure system 91 thus reducing the fluid pressure on the fluid extendible means 50. All this of course is accomplished without stopping the drive shaft 47 thus obviating the necessity of shutting ed the. main powersource and stopping the drive shaft 47. This results in agrcat saving in power and much freedom in the operation of the pump. W 7

With reference to Figures 4, 5, 6, 7 and 8, these figures illustrate a modification of the fluid pump previously described which incorporates the valving ring illustrating the invention. The following description deals mainly with the valving ring and its function in the pump. A valving ring 107 best seen in Figures 7 and'8 has been incorporated within the pump 15 in'an annular. recess formed in the inner cylindrical surface of the rotor 23-, as shown in Figures 4 and 6. The valving ring 187 is mounted coaxial with the insert member 18 and is located within the rotor 23. and is adapted for movement with the rotor. The valving ring comprises an annular member 103 having cylindrical internal and external surfaces 127, 128, first and second end surfaces 130, 13-1, and first and second annular channels 109, 110. The first annular channel 109, as shown in Figs. 7 and 8, is substantially concentric with annular member 108 and generally normal to the second end sur 'face '131. It comprises first and second axially extending side walls 132, 133, and a radially extending bottom Wall 134. The first or outermost side wall 132 extends from bottom wall 134 to the second end surface 131. The second side wall 133 extends from bottom .wall 134 toward the second end surface 131, but terminates short thereof in an annular radial shoulder 135 which is ing wardly spaced from the second surface 131 to form a passageway between the annular groove 139 and the internal surface 127 of the valve ring. The channel 110 is an outwardly opening circumferential groove formed by an axially extending bottom wall 117 and spaced opposed radially extending side walls 118, 119. As best noted in Figure 4 the valvingring 107 is lo cated between the secondary control pump 63 and the fluid ge xtendible 50. The first annular channel 199 is provided with a series of circumferentially aline'd first valve ports 114- which are equally spaced for-chinmunication with first alternate fluid chambers 115 in the first pump pistons 27. The fluid chambers which are in-' cluded within the fluid extendible means 50 have been separated into two sets or groups. The first group of alternate fluid chambers has been indicated by the reference numeral 115 and the second group of fluid chambers has been indicated by the reference numeral 116.

The second annular channel 110 is provided with secondvalve ports 120 which second valve ports communicate with the second group of alternate fluid chambers 116 which fluid chambers are located in the first pump pistons 27 other than the fluid chambers which the first valve ports 114 communicate with. In other words the first valve ports 114 provide fluid communication between the first annular channel 109 and the fluid cham bers 115 which reside within the first pump pistons 27 and the second valve ports 120 provide fluid communication between the second annular channel 110 and the second group of fluid chambers 116 or the remainder of the timid chambers which are located within the remaining first pump pistons 27.

A channel connecting passageway 123 best seen in Figure 8 extends between the first and second annular channels 109 and 110, respectively, for providing fluid communication therebetween. More particularly, passageway 123 extends between bottom wall 134 of first annular channel 109 and side wall 118 of second annular channel 110. A spring loaded valve member 124 resides within the channel passageway 123 and is movable between a first and a second position. The spring loaded valve member 124 when in the first position permits passage of fluid from the first annular channel 109 to the second annular channel 110, and in the second position as shown in Figure 8 the spring loaded valve member 124 prohibits passage of fluid from the first to the second annular channel.

A relief pressure valve 111, similar to the valve 79 shown in Figure 1 is provided in a relief passage 129 extending between side wall 119 of second annular channel 110 and first end surface 130 and is biased closed by a spring 112 and its purpose is to prevent undue pressure build up in the second annular channel 110. When this valve 111 is forced open by fluid pressure the fluid is transmitted to the primary housing 16. The exhaust conduit means 78 used in conjunction with the pump shown in Figures 4, 5 and 6 connects the exhaust chamber 73 of the secondary pump 63 and the first annular channel 109 in the valving ring 107 whereby the fluid pumped by the secondarypump 63 is delivered initially to the first annular channel 109. The fluid under pressure thereafter travels into the channel connecting passageway 123 and overcomes the spring loaded valve member 124 thereby moving this valve member to the first position and thus delivering fluid under pressure to the second annular channel 110. Thus, fluid under pressure travels from the first annular channel 109 through the first valve ports 114 to the first group of alternate fluid chambers 115 and the fluid under pressure in the second annular channel 110 travels therefrom through the second valve ports 120 into the second group of fluid chambers 116. As a result of the fluid pressure communicated to the fluid chambers 115 and 116 the fluid extendible means 50 are actuated and the first and second pump pistons 27 and 28, respectively, in all of the pump cylinders are maintained in engagement with the cam means 33. i

The pump cylinders in the pump of Figures 4, 5 and 6 which correspond to the pump cylinders 24 of the pump shown in Figures 1, 2 and 3 have been divided into two groups of pump cylinders indicated by the reference numerals 25 and 26, respectively. The pump cylinders 25 carry the first set or group of pistons 27 which have the chambers 115 therein and the pump cylinders 26 carry the second set or group of have the chambers 116therein.

As will be noted in the pump of'Figure 4 the two discharge passageways 39 and 40 are not connected together and the pump therefore provided two sources of fluid supply under pressure. Port means 44 are located in the rotor 23 for providing alternate communication between the pump cylinders 25 and the discharge and intake passageways, 40 and 38, respectively, and port means 45 are located in the rotor 23 for providing alternate communication between the pump cylinders 26 and the discharge and intake passageways, 39 and 38,

pistons 2'7 which:

respectively. The port means 44 slope toward the right end of the pump and the port means 45 slope toward the left end of the pump as seen in Figure 4. 1

The piston collapsing conduit means is connected to the exhaust conduit means 78 of the secondary pump 63 and connects the same to a low pressure system 91.- When the valve means 93 is in the first position fluid communication between the exhaust conduit means 78 and the low pressure system 91 is permitted whereby fluid which is delivered by the secondary control pump 63 is exhausted to the low pressure area 91 and the fluid pressure in the first group of fluid chambers is re duced. The fluid pressure in the second annular channel 110 along with the force of the spring serves to maintain and hold the spring loaded valve 124 in the second position'whereby fluid pressure is prevented from escaping back to the first annular channel 109 through the channel connecting passageway 123 and therefore fluid pressure is maintained in the second group of fluid chambers 116. In the event that there is normal leak age from the second annular channel 110 the pressure 1 therein will be maintained by the normal leakage of high pressure fluid from the pump cylinders 26 into the chambers 116 and hence down into the channel 110. This pressure will be prevented from exceeding a predetermined value by the spring loaded valve 111 which opens up to discharge into the pump housing. It will thus be seen that by utilizing the valve ring 107 in combination with the pump 15 which has been herein disclosed, that the first and second pump pistons 27 and 28 in the pump cylinders 25 may be collapsed or rendered ineffective for pumping purposes by merely actuating the valve means 93 to the first position. If it is deemed desirable to operate the pump utilizing allof the first and second pump pistons in all of the pump cylinders 25 and 26 it is merely necessary to move the valve means 93 to the second condition whereby all of the pump pistons will be effective for the pumping operation.

It will be readily observed from the description of this latter pump that two fluid requirements may be supplied by this pump since neither of the discharge passageways are connected together. This same principle may be utilized to supply more than. two fluid requirements. It would also be possible to connect both of the discharge passageways together to' supply a single fluid requirement but in this case it would be necessary to provide a check valve or something similar in the discharge passageway which would be rendered ineffective when a portion of the pump pistons is collapsed, so that high pressure fluid from the other discharge passageway would not leak back up into the cylinders and force the collapsed pistons back out against the cams. It is also possibleto vary the volume and pressure output of the pump by varying the size of the pump cylinders and the'strokeof the pump pistons. As a consequence the pump shown in Figure 4 may deliver different volumes and pressures' of oil from each of the separate discharge passageways.

Although this invention has been described in its pre-- ferred form with a certain degree of particularity, it is understood that the present disclosure of the preferred form has been made only by way of example and that numerous changes in the details of construction and the combination and arrangement of parts may be resorted 7 to wi u -depar n fr m th spi it and the swi the invention as hereinafter claimed.

What is claimed is:

1. A valving ring comprising an annular member having an inner and an outer surface and having first and second annular channels therein, said first annular channel having a bottom wall and having first and second side walls. extending generally parallel to said inner surface and said second annular channel extending to said outer surface, said first annular channel having first valve ports extending therefrom to said outer surface, said second annular channel having second valve ports extending therefrom to said outer surface, said first valve ports and said second valve ports being disposed in al ternating circumferentially spaced relationship about said outer surface of said annular member, a channel connecting passageway extending between said first and second annular channel, a spring loaded valve member, residing within said channel connecting pasageway and movable between a first and a second position, said valve member in said first position permitting passage of fluid from said first to said second channel and in said secand position prohibiting passage of fluid from said first to said second channel, a relief passageway extending between said second annular channel and the exterior of said valving ring, a spring loaded relief pressure valve residing within said relief passageway and movable between a first and a second position, said relief valve in said first position permitting passage of fluid through said relief passageway and in said second position prohibiting passage of fluid through said relief passageway.

2. A valving ring comprising an annular member having an inner and an outer surface and having first and second annular channels therein, said first annular channel extending to said inner surface and said second anular channel extending to said outer surface, said first annular channel having first valve ports extending therefrom to said outer surface, said second annular channel having second valve ports extending therefrom to said outer surface, a channel connecting passageway extending between said first and second annular channel, a spring loaded valve member residing within said channel connecting passageway and movable between a first and a second position, said valve member in said first position permitting passage of fluid from said first to, said second channel and in said second position prohibiting passage of fluid from said first to said secondchannel. 3. A valving ring comprising an annular member having first and second annular channels therein, said first annular channel having first valve ports and said second annular channel having second valve ports, a channel connecting passageway extending between said first and second annular channel, valve means residing within said channel connecting passageway and movable between a first and a second position, said valve means in said first position permitting passage of fluid from said first to said second channel and in said second position prohibiting passage of fluid from said first to said second channel.

4. A valving ring adapted for controlling the flow of pressure fluid to first and second sets of hydraulically controlled mechanisms comprising, an annular member having first and second annular channels, substantially concentric with said member, said first channel being positioned and adapted for receiving pressure fluid, a series of equally spaced circumferentially alined ports, formed in said annular member and extending from said first channel and opening on the outside of said member for conducting pressure fluid, a second series of equally spaced circumferentially alined ports in said first passageway for permitting flow of pressure fluid from said first channel to said second channel and for maintaining fluid under pressure in said second channel upon reduction of fluid pressure in said first channel, a second fluid passageway formed in said member and extending from said second channel to an end of said member, and a one-way relief valve means in said second passageway for limiting the pressure of fluid buildup in said second channel.

5. A valving ring adapted for insertion into a rotor recess of a hydraulic apparatus and comprising, an annular member having an inner surface, an outer surface, first and second end surfaces, and a first and second annular channel formed therein, said first annular channel being formed in said second end surface generally coaxial with said annular member and having a bottom wall, a first side wall, a second side wall, said first side wall extending between said second end surface and said bottom wall, said second side wall extending toward said second end surface in generally spaced opposed relationship to said first side wall, an annular radial shoulder positioned inwardly from said second end surface and extending between said second side wall and said inner surface of said annular member, said second annular channel being formed radially into said outer surface and having a bottom wall and first and second side walls extending between said bottom wall and said outer surface in generally parallel spaced relationship to each other, a plurality of radially extending first port means extending between said first side wall of said first annular channel and said outer surface in circumferentially spaced relationship about said annular member, a like number of second port means extending axially from said second annular channel into substantially circumferential alignment with said first port means in alternating relationship therewith, a connecting passageway extending between said bottom wall of said first annular channel and said first side wall of said second annular channel, spring-loaded ball valve means in said connecting passageway and being movable from a first spring loaded position to a second position in response to pressure in said first annular channel for preventing the flow of fluid between said first channel and said second cavity when in said first position and permitting the flow of fluid between said first channel and said second channel when in said second position; a relief passageway extending between said second side wall of said second annular channel and said first end surface, and a spring-loaded relief valve disposed within said relief passageway and movable from a first spring-loaded position to a second position in response to pressure in said second annular channel for preventing the flow of fluid through said re lief passageway when said relief valve is in said first position and permitting the flow of fluid through said relief passageway when said relief valve is in said second position.

References Cited in the file of this patent UNITED STATES PATENTS 1,669,976 De'Leeuw May 15, 1928 1,900,735 Richardson Mar. 7, 1933 1,935,376 Prellwitz Nov. 14, 1933 2,381,910 Joy Aug. 14, 1945 

